Reduction jaw crushers



0. C. GRUENDER REDUCTION JAW CRUSHERS Sept. 5, 1961 6 SheetsSheet 1 Filed April 19, 1961 INVENTOR. 056G? 6161716126167" BY gi /m 1d 6 Sheets-Sheet 2 INVENTOR.

05641" C firzleizaei" Sept. 5, 1961 o. c. GRUENDER REDUCTION JAW CRUSHERS Filed April 19, 1961 Sept. 5, 1961 o. c. GRUENDER REDUCTION JAW CRUSHERS 6 Sheets-Sheet 3 Filed April 19, 1961 MMEIL INVENTOR. Oscar- 6T fii 'aelzder' P 5, 1961 o. c. GRUENDER 2,998,936

REDUCTION JAW CRUSHERS Filed April 19, 1961 6 Sheets-Sheet 4 FIEEJ d6;

p 1961 0. c. GRUENDER 2,998,936

REDUCTION JAW CRUSHERS Filed April 19, 1961 6 Sheets-Sheet 5 FIEE I N V EN TOR. Oscar C Graevzaer Sept. 5, 1961 o. c. GRUENDER REDUCTION JAW CRUSHERS 6 Sheets-Sheet 6 Filed April 19, 1961 INVENTOR. 05(0)" CGraeIIa Pr United States Patent 2,993,936 REDUSTIGN SAW CRUSHERS Oscar C. Grnender, H00 E. Capital Drive, Apt. 2, Milwaukee 11, Wis. Filed Apr. 1%, 1961, Ser. No. 100,044 8 Claims. (Cl. 241-140) This invention relates to improvements in jaw crushers, and more particularly to a jaw crusher used for the continuous secondary reduction of rock or the like.

It is an object of the invention to provide a double acting jaw crusher which will reduce power consumption.

Another object of the invention is to provide a rock crusher for secondary reduction of rock, or the like, which is capable of producing a fine product.

A further object is to provide a rock crusher which will prevent undue pressures from developing.

A further object is to provide a rock crusher having a continuous crushing operation which will be more economical to operate than those now in use.

A still further object is to provide a jaw crusher having lower maintenance cost.

Still further objects will become apparent upon considering the following specification, which, when taken in conjunction with the accompanying drawings, illustrates a preferred form of the invention.

In the drawings:

FIG. 1 is a side elevational view of a jaw crusher embodying the-present invention with the drive pulley removed;

-FIG. 2 is a transverse cross-section taken on the line 2--2 of FIG. 1, looking in the direction of the arrows;

'FIG. 3 is a vertical cross-section taken on the line 3-3 of FIG. 2, looking in the direction of the arrows,

FIG. 4 is a transverse cross-section through one of the stationary jaws of the crusher and is a cross-section taken on the line 44 of FIG. 3;

FIG. 5 is a plan view of the adjusting shim used in connection with the stationary crusher jaw.

FIG. 6 is a transverse cross-section taken on theline 66 of FIG. 2, looking in the direction of the arrows; and

FIG. 7 is a motion diagram of the moving jaw head, portions of the stationary jaws being shown in section and the eccentric shaft and pivot shaft being shown in end elevation.

Referringto the drawings, indicates a substantially rectangular frame, comprising the vertical side walls 22 and the vertical end walls 21 connected together to form the frame 20.

The rectangular frame 20 has flanges 2424 reinforced by webs 25 at the lower end of the frame and flanges 2727, reinforced by webs 28 at the upper ends. The frame 20 may be mounted on any suitable founda tion, the flanges 24 being provided with suitable holes to accommodate foundation bolts.

The side Walls 2222 are provided with alined hubs or sleeves 3030, projecting outwardly from the walls 2222 to receive bearing sleeves 31--31. The bearing sleeves 3'131 are provided with flanges 32-32 which receive screws 33 to secure the sleeves in position.

Two bushings 35 of bronze or-other low friction mate rial are provided for each bearing, each one being flanged at its outer end at 36 and extending in opposite directions into the sleeve 31, the inner ends being separated to leave a channel 38, for lubrication, the lubrication system being described in detail below.

An eccentric shaft 40' includes a pair of shaft portions 41, conforming to the bushings 35, and an enlarged cylindrical connecting shaft portion 44 formed eccentrically on the inner ends of the shaft portions 41- 41 to form the eccentric.

Flywheels 46-46, which may be counterbalanced as shown at 47, are secured by keys 48 to the outer ends of the shaft portions 41--41. Any suitable source of power (not shown) may be utilized to drive the, crusher through the flywheels.

Secured to each end ofthe shaft 40 between the bushings 35 and the flywheels 46 is an oil flinger 50 which is surrounded by a cover plate 51. The cover plate 51 is held in place by screws 33. The oil flinger 50 and cover plate 51 combine to prevent the loss of oil from the bushings 3'5 and preclude the entrance of dust and grit into the bearings.

A movable jaw head, generalh designated- 55, is mounted for gyration on the eccentric portion 44 of the shaft 40. The jaw head 55 is formed with a cylindrical bearing housing 56 fitted with suitable bushings 57. Side walls 59 extend upwardly from the bearing portion 56 and are formed with the outwardly and downwardly flared portions 60, tapered inwardly as at 61.

The enlarged central portion 61 of the jaw head 55 between the flared portions 60 forms a housing for a pivot shaft 65. A vertical connecting rib 66, joining the eccentric housing 56 with the pivot shaft housing, provides reinforcement for the entire jaw head. Downwardly extending ribs 6868', FIGS. 3 and 7, are formed on the lower sides of the flared portions 60 to connect the side walls 59-59.

The bushings 57 for the eccentric shaft portion .44

are flanged as shown at 69 and extend in opposite directions into the cylindrical bearing housing 56 of the jaw head, leaving a channel 70 between the inner ends of the bushings to provide for adequate lubrication, to be described below.

The pivot shaft 65 is received in an aperture in the enlarged central portion 61 of the jaw head and is secured in place therein by headless screws .71 to prevent rotation of the shaft 65 in the jaw head. The extended end portions of the pivot shaft 65 are received in bearings 72 made of metal having a low coeflicient of frice tion. The bearings 72 have vertical bearing surfaces 73 in vertical sliding contact with bearing surfaces 75 of the bearing housings 76, as shown in FIG. 6. The bearing housings are secured to the side walls 22 of the frame and to the upper flanges 27 by screws 77 and 78 ('FIG. 1).

An inner closure plate 81 is attached to the bearing housing 76. An elongated aperture '83, FIG. 2, provides for vertical movement of the pivot shaft 65'.

The inner closure plate 81 has a circular projection 84 to receive flexible hose connections 8585, each flexible hose connection being fastened by means of clamps or binding Wires to both the projection 84 and cooperating cylindrical projections on the upper partof the jaw head 55 concentric with the shaft 65. The two hoses 85-85 prevent the entrance of dust and grit into the bearings 72.

A sealing plate 87 bears against the inner surface of the closure plate 81 and is urged into engagement by springs 86 carried in the bearings 72. The sealing plate is provided with a circular aperture to accommodate the pivot shaft 65, the sealing plate covering the elongated movement of the eccentric shaft 40 to produce a simultaneous oscillatory and gyratory or wave-like movement of the movable crusher jaws.

The lower movable jaw members 92 (FIGS. 2 and 3) are secured to the jaw head 55 by a wedge plate 93 which is secured to the jaw head by screws 94, with the jaw members 92 wedged between a toe 95 on the outer end of the outwardly and downwardly flared portions 60 of the movable jaw head and the wedge plate 93.

In order to supply dust tight enclosures for the bushings 35 and to provide-for the return of lubricating oil to its source, there is provided a metal trough 98, having a flange 99 (FIG. 3) at the top of the trough, with end elements 100. The end elements 100 have openings which receive the bearing sleeves 31 which support the trough.

The end elements 100 have inwardly extending flanges 101 in the plane of the flanges 99 of the trough 98.

A dust guard 102 made of highly flexible material such as rubber is secured between the flange 99 and the flange 101 at the lower end of the guard and the side walls 59 and the ribs 68 of the jaw head 55 at the upper end of the guard 102.

The dust guard is looped between its upper and lower connection points to provide amply for the movement of the jaw head 55 without the necessity of the material stretching, thus providing against the possibility of dust entering the bushings 35 and 57.

The trough 98 is provided with two drain pipes 103 to return oil from the bushings 35 and 57 to the oil supply source.

The frame 20 is provided with a yieldable jaw support. generally designated 104 (FIG. 1), formed with end walls 105 and side walls 106, a lower flange 107, an upper flange 108 and ribs 109. The lower face at each end of the flanges 107 is provided with a convex surface 110 which contacts a renewable wear plate 111 secured to the upper flange 27 of the frame 20 by welding or the like.

Each of the flanges 107 is provided with a downturned finger 113. with a convex inner surface contacting the wearing member 111. The combination of the convex surfaces 110 on the lower flanges with the convex surfaces on the fingers 113 permits the yieldable jaw support 104 to tilt at either end of the frame 20 to relieve excessive pressure due to foreign matter passing through the crusher or the like, while retaining it against lateral displacement.

In order to retain the yieldable jaw support in position as the rock is being crushed, a plurality of compression springs 1 15 are mounted on tension bolts 116. The bolts 116 pass through the lower flange 107 of the yieldable jaw support 104 and through an abutment plate 118. The bolts 116 are provided with nuts 1'17 bearing on top of the lower flange 107, and nuts 1'19 bearing on the abutment plate 118. The compression in the springs 115 serves to retain the yieldable jaw support 104 firmly on the frame 20 under normal working conditions but permits it to yield to excess pressures and thus prevent breakage.

The stationary jaw member assembly, generally designated 120, is bolted to the vertical side walls 105 of the yieldable jaw support 104 by screws 121.

The stationary jaw member assembly 120 is formed by a vertical wall 124, an upwardly and inwardly flared wall 125 formed integrally on the lower end of the wall 124, a top plate 127 formed integrally on the top of the wall 124 and extending horizontally inwardly. and side walls 126 at the opposite ends of the vertical wall 124 and the top plate 127. An outwardly extending projection 128 is formed at the junction of the walls 124 and 125 and extends under the end walls 105 of the yieldable jaw support 104.

A stationary jaw 130 (FIG. 4) is positioned above each of the movable jaw members 92 to co-operate therewith in the crushing action. The jaw 130 has a central boss 131 formed to receive a steel insert 132. The insert 132 is threaded to receive the lower end of a tension bolt 134. A backing plate 136 is attached to the stationary jaw 130 by a soft metal insert 135. An adjustment shim 137 (FIG. 5) may be inserted between the backing plate 136 and the wall either to compensate for wear of the jaws 92 or 1130, and to vary the opening between the jaws. The shim 137 which is shown in plan in FIG. 5, is provided with a slot 138 to receive the tension bolt 134. Nuts 139 are provided for the upper free end of the tension bolt to retain the parts of the stationary jaw assembled with the jaw support 120. While only one shim is shown, adjustment shims of varying thickness are provided with the machine to vary the spacing between the jaws.

A cover plate 145 is secured to the top plate 127 by bolts 146 and covers the opening between the plates 125 and 127 while at the same time serves as one face of a hopper into which the rock may be loaded for crushing by the machine.

A guard member 141 is secured to the flange 108 by screws 142. Each guard member 141 has a vertical extension 143 which depends from the guard 141 and abuts the ends of the jaw members 92 and with a minimum clearance therebetween to prevent sideways escape of material from between the ends of the jaws 92 and 130 and thus insure proper and uniform crushing. The vertical extension 143 of the guard members 141 and the cover plate 145 form the receiving hopper for the material to be crushed, from where it is fed by gravity into the crushing cavities.

Oil under pressure is supplied to all bearings by an oil tank and oil pump (not shown). Oil from the tank is forced under pressure from the pump (not shown) through a pipe 148 (FIG. 1) through the Wall of the hub 30 and the bearing sleeve 31 as at 150( FIG. 1) to a long tudinal groove 151 in the bearing sleeve. The groove 151 connects with channel 38 formed between the bushings 35. From the channel 38 the oil flows in both directions to the bushings 35, the oil escaping at the ends of the bushings. Likewise, oil flowing through the channel 38 flows through a duct 152 which connects with an oil passage 153 in the center of the shaft 40. From the passage 153 oil flows through a duct 154 to the channel 70 and thence in both directions to the bushings 57.

Also from the passage 153, oil flows through a duct 155 to the channel 38 and then flows in both directions to lubricate the bushings 35. The oil passage 153 is closed at the end by a plug 155'.

Oil from the inner bushings 35 and from bushing 57 drains into the trough 98 and to the drain pipe 103. Oil from the outer bushings 35 flows to the inside of cover plate 51 and thence to the drain pipe 156 connecting with the drain pipe 103, which is the drain pipe from trough 98. From the drain pipe 103, the oil from. all the bearings flows by gravity to the oil supply tank.

The lubrication for the bearings 7272. is provided by oil from a pipe 157 (FIGS. 1 and 6) which is supplied by the pipe 148 to an oil reservoir 158 (FIG. 6). The oil flows from the reservoir 158 through a horizontal aperture 159 through an annular aperture 160 which serves to lubricate the shaft bearing and to transmit part of the oil through the continuing aperture 159 to a second oil reservoir 162.

Oil is returned to the oil tank (not shown) through a drain pipe 163. A similar lubricating system is provided for the opposite bearing 72.

Operation The present crusher is intended primarily for use for the secondary crushing or reduction of material following the primary type crusher. It can be fitted with crushing jaw members of various size throat openings and length to suit the size of the feed and to effect the required ratio of reduction.

The material to be crushed is delivered in an unmixed state to the feed hopper 143-145, from whence it flows by gravity into the crushing cavities.

The machine is put in operation by rotating the shaft 40, which causes the center B of the eccentric portion 44 of the shaft to rotate around the axis A of the shaft 40 as shown in the motion diagram FIG. 7.

Referring again to FIG. 7, the eccentricity E determines the radius of the circle C about which the center B of the eccentric portion 44 of the shaft rotates clockwise as indicated by the arrow R.

Rotation of the eccentric shaft causes the center V of the pivot shaft 65 to oscillate on the line or axis XX, FIGS. 3 and 7. For a complete rotational cycle of the eccentric shaft 40, the center V of the pivot shaft 65 moves from point V1 to V2 on the axis XX and then back again from point V2 to V1, FIG. 7.

The oscillation of the pivot shaft 65 combined with simultaneous gyration of the jaw head 55 at its lower end, results in a movement of the crushing jaws 92 whereby the high point of the crushing jaws advances circumferentially in a progressive, wave-like movement toward the stationary crushing jaws 130.

Referring to FIG. 7, when the high point H of the eccentric shaft portion 44 reaches its low point, or position P1, it lies on the axis XX with point H below the center of rotation A of the eccentric shaft; and the position of the two crushing jaws 9292 relative to the fixed crushing jaws 130130 is shown in dotted lines at MM At this position material from the hopper 143-145 flows into the crushing cavities between the jaws, and material continues to enter the right hand crushing cavity even though the high point H has rotated 90 degrees from the axis XX.

When the eccentric shaft has rotated clockwise 90 de grees about the fixed center A, the high point I-I lies on the fixed horizontal axis YY passing through the center A of the shaft 4%]. During this 90 degree rotation of the eccentric shaft 40, the crusher jaw 92 (shown on the left in FIG. 7) has moved upwardly from the dotted line position M to the full line position D, and the crusher jaw 92 at the right in FIG. 7 has travelled from the dotted line position M to its full line position D It will be noted that the major portion of the crushing action in the left hand cavity occurred in the first quadrant of the rotation or from P1 to P2.

On the other hand, it will be observed that the crusher jaw 92 at the right in FIG. 7 has moved upwardly only from position M to D during the rotation of the eccentric shaft 40 through the same quadrant, and hence very little crushing is done in the right hand cavity while the crushing practically is completed in the left hand cavity and hence the power to operate the crusher is kept at a minmum.

During the next quadrant of rotation of the shaft 40, the eccentric portion 44 of the shaft rotates about the center A until the high point H reaches its point of maximum height, or position P3, at which point H lies on the vertical axis X-X of the machine. On the completion of this quadrant of rotation, the movable jaw 92 on the left hand side of the machine, as seen in FIG. 7, has advanced to the dotted line position N to complete the crushing action for that cavity. This is the position of the movable jaws 92 as shown in FIG. 3.

Similarly, the movable jaw 92 on the right hand side of FIG. 7 has also advanced to the dotted line position N and that movable jaw also has substantially completed its crushing action.

Since the crushing on the opposite sides of the machine occurs in approximately one quarter rotation of the eccentric shaft, and since these working quadrants are not the same, it follows that a minimum of power will serve to operate the machine.

The movement of the jaw head is of considerable amplitude so that a relatively thick ribbon of material enters the crushing cavities. However, the speed of the jaw head is such as to limit the amount of material fed from the hopper into the crushing cavities.

After the material receives its first impact, it drops by gravity to a lower position on the movable jaws, contacting the jaws when they have receded approximately to the point of farthest recession from the stationary jaws. The material therefore moves in rhythmic sequence receiving a plurality of successive impacts on its passage through the crushing cavities, each of the impacts serving toreduce the size of the materialas it passes through the cavities.

In the event some uncrushable substance such as tramp steel enters the crushing cavity, springs will then compress to permit the yieldable jaw support to tilt on the frame 20 and permit the uncrushable substances to pass through the machine without damage to any of its parts.

Having thus described the invention, it will be realized that the drawings show merely a preferred embodiment thereof, and that various changes in size, shape or arrangement of parts may be resorted to without departing from the spirit of the invent-ion'o-r the scope of the subjoined claims.

That which is claimed as new and is desired to be secured by United States Letters Patent is:

1. In a jaw crusher, a frame, a normally stationary jaw mounted on said frame, a movable jaw head mounted in said frame, a crushing jaw member mounted on said jaw "head and underlying said stationary crushing jaw to form a crushing cavity therebetween, means to support the jaw head and to gyrate it at its lower end, said jaw head pivoted at its upper end to provide for limited vertical and oscillating movement of the jaw head adjacent its pivot end, the pivot center being above the gyrating means and always lying on the fixed vertical axis passing through the fixed center thereof, the said gyrating means at the lower end of the jaw head effecting simultaneous oscillatoryand-gyratory motion of the-movable crushing jaw member.

2. In a jaw crusher, a frame, a normally stationary jaw mounted on said frame, a movable jaw head mounted in said frame, a crushing jaw member mounted on said jaw-head and underlying said stationary crushing jaw to form a crushing cavity therebetween, means to support the jaw head and to gyrate it at its lower end, said means including a fixed center, said jaw head pivoted at its upper end to provide for its limited vertical and oscillating movement adjacent its pivot end, the pivot center lying on and movable in all positions on a verticalaxis of the jaw crusher passing through the fixed center of the gyrating means, the said gyrating means at the lower end of the jaw head effecting simultaneous oscillatory and gyratory motion of the movable crushing jaw member.

3. In a jaw crusher, a frame, a normally stationary jaw mounted on said frame, a movable jaw head mounted in said frame, a crushing jaw member mounted on said jaw head and underlying said stationary crushing jaw to form a crushing cavity therebetween, means to support the jaw head and to gyrate it at its lower end, said jaw head pivoted at its upper end to provide for its limited vertical and oscillating movement adjacent its pivot end, the pivot center lying on the vertical axis of the jaw crusher passing through the fixed center of the gyrating means, and means to restrain lateral displacement of the pivot center on the vertical axis, the said gyrating means at the lower end of the jaw head elfecting simultaneous oscillatory and gyratory motion of the movable crushing jaw member.

4. In a jaw crusher, a frame, a movable jaw head in-.

and overhanging said crushing face and forming a crushj ing cavity therebetween, means to gyrate the jaw head at its lower end, said jaw head pivoted at its upper end to provide for its limited vertical and oscillating movement adjacent its pivot end, means restraining lateral movement of the pivot/the pivot center lying on the vertical axis of the jaw crusher passing through the fixed center of the gyrating means, the high point of the jaw head crushing face moving progressively around the fixed center of the gyrating means, the amplitude of the jaw head movement normal to its crushing face being of substantially the same magnitude at the entrance and exit openings of the crushing cavity commencing with the point of farthest recession of the said movable jaw head and when the rotating center of the gyrating means is directly below the fixed center of the gyrating means and lies on the said vertical axis and is rotated 180 degrees from that position.

5. A jaw crusher of the character described comprising, a frame, a yieldable jaw support mounted above said frame, dual stationary crushing jaws mounted opposite each other on said yieldable ja'w support, a movable jaw head mounted in said frame, a pivot member in the jaw head to provide for limited vertical and oscillating movement of the jaw head adjacent the pivot end of the jaw head, dual crushing jaw members mounted on the said jaw head on opposite sides of said pivot member and underlying the dual stationary crushing jaws to form dual crushing cavities therebetween, a single hopper located in said yieldable jaw support feeding material to the dual crushing cavities, and means to actuate said jaw head to produce simultaneous oscillatory and gyratory motion of said crushing jaw members to produce a wave-like upward thrust of the crushing jaw members.

6. A jaw crusher of the character described comprising, a frame, a yieldable jaw support mounted on top of said frame, dual stationary crushing jaws mounted opposite each other on said yieldable jaw support, a movable jaw head mounted in said frame, a pivot member in the jaw head to provide for limited vertical and oscillating movement of the jaw head at the pivot end of the jaw head, dual movable crushing jaws mounted on the said jaw head and underlying the dual stationary crushing jaws and forming dual crushing cavities therebetween, a single hopper located in said yieldable jaw support feeding material to the dual crushing cavities, resilient means to secure said yieldable jaw support to said frame while permitting limited movement of the jaw support to relieve excessive crushing pressures in the dual crushing cavities, and means to actuate said jaw head to produce simultaneous oscillatory and gyratory motion of the said dual movable crushing jaws whereby the high point of the crushing jaws advances progressively around the enter of the gyrating means.

7. A jaw crusher as described in claim 6, including a vertically inclined abutment means on the yieldable jaw support and frame to prevent lateral displacement of the yieldable jaw support in its limited vertical movement in response to excessive crushing pressures in the crushing cavities.

8. In a dual cavity jaw crusher, a frame, dual stationary crushing jaws symmetrically mounted opposite each other on said frame, a movable jaw head mounted in said frame having dual symmetrical crushing jaw faces opposed to the said stationary crushing jaws and forming crushing cavities therebetween, means to receive material fed by gravity into the crushing cavities, means to gyrate the jaw head at its lower end, said means including a fixed center, said jaw head pivoted at its upper end to provide for its limited vertical and oscillating movement adjacent its pivot end, the pivot center restrained to lie on a vertical axis of the jaw crusher passing through the fixed center of the gyrating means, the crushing jaw faces being positioned symmetrically to said vertical axis, the area of crushing impact moving progressively around the fixed center of the gyrating means in a wave-like movement, the amplitude of the crushing impact being of the same magnitude on each side of the said vertical axis.

References Cited in the file of this patent UNITED STATES PATENTS 2,097,906 Wettlaufer Nov. 2, 1937 2,131,801 Gruender Oct. 4, 1938 2,670,141 Anderson Feb. 23, 1954 FOREIGN PATENTS 2,993 Great Britain of 1874 372,645 Great Britain May 12, 1932 605,475 Germany Nov. 14, 1934 

